EP2551504A1 - Piston et segment répartiteur d'huile pour moteur à combustion interne à piston élévateur - Google Patents

Piston et segment répartiteur d'huile pour moteur à combustion interne à piston élévateur Download PDF

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Publication number
EP2551504A1
EP2551504A1 EP11175158A EP11175158A EP2551504A1 EP 2551504 A1 EP2551504 A1 EP 2551504A1 EP 11175158 A EP11175158 A EP 11175158A EP 11175158 A EP11175158 A EP 11175158A EP 2551504 A1 EP2551504 A1 EP 2551504A1
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EP
European Patent Office
Prior art keywords
piston
ring
piston ring
combustion chamber
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP11175158A
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German (de)
English (en)
Inventor
Matthias Stark
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP11175158A priority Critical patent/EP2551504A1/fr
Publication of EP2551504A1 publication Critical patent/EP2551504A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F5/00—Piston rings, e.g. associated with piston crown
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/08—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction with expansion obtained by pressure of the medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F16J9/20—Rings with special cross-section; Oil-scraping rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F16J9/22—Rings for preventing wear of grooves or like seatings

Definitions

  • the invention relates to a piston, a piston ring and an oil distribution ring for a piston of a reciprocating internal combustion engine, in particular two-stroke large diesel engine according to the preamble of independent claims 1 and 15.
  • pistons for example, but not only for large diesel engines are usually equipped with a pack of several, each in a piston ring groove superimposed piston rings.
  • the known piston ring packings include at least two piston rings, but usually three, four or even five piston rings, depending on the size and / or power of the engine or depending on the requirements or the specific operating conditions under which the machine is operated.
  • the trend is more and more towards piston ring packings with as few piston rings as possible.
  • piston ring packings with only two piston rings are now being used with advantage. In very special cases, even pistons with only a single piston ring are possible in principle.
  • the piston rings which perform various functions, such as the guidance of the piston in the cylinder, the distribution and / or stripping a lubricant on the running surface of the cylinder, the sealing of the combustion chamber against the piston underside, etc., are exposed to considerable loads during operation.
  • the piston rings are directly in frictional contact with the cylinder surface, the combustion pressure must be absorbed by the piston rings and the piston rings are thus exposed to significant thermal, mechanical and chemical stresses.
  • the piston ring package does not take over the centering of the piston in the cylinder, as is often assumed erroneously. Because of the design, this is not possible at all.
  • the piston rings themselves are always guided centered in the cylinder automatically with respect to the radial direction, since their outer diameter is always chosen slightly larger than the inner diameter of the cylinder in non-installed position, the diameter of the piston rings is so elastically variable that the Kolbering in Circumferential direction is always pressed under a predetermined pressure against the cylinder wall.
  • the inner diameter of the piston rings is greater than the outer diameter of the piston ring grooves on the piston, in which the piston rings are arranged on the piston.
  • the piston ring package or the individual piston rings are thus arranged "freely floating" with respect to the piston or the piston ring grooves. This is also imperative because the piston rings are not allowed to be in constant frictional contact with the Kolbenringnute, otherwise the piston ring would no longer be optimally guided on the cylinder wall, it can lead to jamming on the cylinder wall and / or in the Kolbenringnute and thus to serious damage, to the dreaded scuffing can come.
  • the cylinder lubrication is performed by lubricating in the reciprocating piston or realized by provided in the cylinder wall lubricating oil nozzles.
  • combustion residues which can be deposited at various points in the engine.
  • combustion residues represent a significant problem, since the fuel used, namely the heavy oil is loaded with many substances that can lead to solid, liquid and gaseous combustion residues of all kinds.
  • blowby effect Another factor that particularly affects the movement of the "upper" top ring, that is to say that piston ring of the piston ring package which is directly adjacent to the combustion chamber, is the well-known “blow-by” effect.
  • the blowby effect the skilled person understands the fact that the piston rings do not seal absolutely pressure-tight, but a certain amount of gas from the combustion chamber, typically 6-8% of the mass fraction of the gaseous contents of the combustion chamber, on the piston ring package in a more or less uncontrolled manner and Way in Flow direction to the bottom of the piston, whereby the thermal energy contained therein is substantially lost.
  • the pressure energy generated in the combustion chamber in the vicinity of the top dead center is fully usable and not partially flows unused past the piston in the form of a gas stream in the lower part of the cylinder and in the receiver chamber.
  • In the lower part of the cylinder can deposit on the cylinder surface, so not least contaminate the cylinder lubricating oil and in the worst case can lead to damage, such as the dreaded scuffing.
  • an oil distribution ring is very often provided in the piston ring package in practice, which should ensure a better distribution of the lubricating oil on the cylinder surface, in particular in the circumferential direction of the cylinder surface.
  • the known ⁇ lverteilringe which are often referred to as oil scraper or oil collector, collect in addition to the lubricating oil for the Tribosystem harmful solid, liquid and, for. gaseous harmful residues contained in the lubricating oil, which often leads to so-called “scuffing” or “scuffing”, so can lead to serious damage to the cylinder surface, the piston rings and the piston itself.
  • the object of the invention is therefore to propose an improved piston, as well as a corresponding piston ring and a ⁇ lverteilring, with which the disadvantages of the prior art described above are avoided.
  • an improved distribution of the lubricating oil is also to be ensured, while at the same time care should be taken to ensure that the concentration of dirt collected in the oil distribution ring does not increase to a predetermined level.
  • the invention thus relates to a piston for a reciprocating internal combustion engine having at least one cylinder, in particular two-stroke large diesel engine, in which cylinder the piston in the installed state limits a combustion chamber and along a piston axis of the piston in the cylinder between a top dead center and a bottom dead center in the axial direction. and is arranged to be moved.
  • a piston ring packing rubbing against a cylinder wall of the cylinder which comprises a partial ring packing with a first piston ring in a first piston ring groove, which first piston ring between the piston crown and a arranged in a ⁇ lringnute ⁇ lverteilring.
  • a pressure relief means is provided for the controlled pressurization of the oil distribution ring with a predeterminable proportion of a combustion chamber pressure of the combustion chamber, on the partial ring packing.
  • the partial ring packing comprises a first piston ring, which in practice is usually the top ring, ie the piston ring which is arranged closest to the combustion chamber, and is provided with a pressure relief groove or a pressure relief bore on an underside facing an oil distribution ring.
  • the underlying ⁇ lverteilring By the pressure relief groove on the underside of the first piston ring, the underlying ⁇ lverteilring can be acted upon in a controlled manner with a predetermined proportion of the combustion chamber pressure, as by a suitable choice of the geometry and arrangement of the pressure relief a controlled gas flow, so a controlled blow-by can be generated on the ⁇ lverteilring so that the gas dynamic load is not only suitable for the oil distribution, but also on one or possibly below the ⁇ lverteilrings additionally still existing second piston ring is increased appropriately.
  • first piston ring and the second piston ring for example (but not necessary) in particular between the first piston ring and the ⁇ lverteilring in the lateral surface optimized in geometry and arrangement and on the piston ring package or is provided on the piston matched space in the form of a recess.
  • pressure relief means which are preferably formed in a more or less tangential direction, ie in a direction more or less deviating from the radial direction
  • a precisely controlled blowby is allowed and on the other hand more or less strong tangentially arranged pressure relief means generates a preferably vortex-like turbulence of the gas flowing past, which in combination with the on the Gastrom volume-optimized recess between the first and second piston ring on the one hand allows to pressurize the second piston ring with a portion of the combustion chamber pressure that the known from the prior art harmful uncontrolled intrinsic movements of the second piston ring are substantially prevented, so that the second piston ring at a hydrodynamically optimal movement forms assumes a piston according to the invention.
  • the swirling turbulence of the gas flowing past in combination with the volume-optimized recess at the same time also has a positive effect on the circumferential distribution of the lubricant, i. the lubricant distribution is significantly improved, in particular with respect to the circumferential direction of the cylinder.
  • the second piston ring is loaded only with a part of the combustion chamber pressure and also in a controlled manner, this can be carried out practically gas-tight, so that the above-mentioned pressure loss is more or less completely prevented by uncontrolled blowby, and thus the energy generated in the combustion chamber better and more efficient exploitable.
  • the second piston ring can preferably be made thinner and thus less material-consuming and thus more cost-effective, since only a relatively small partial pressure is applied to it.
  • the aim of the hydrodynamically optimized piston ring packing of the present invention is, inter alia, to generate a hydrodynamic pressure that supports the separation of piston ring and cylinder surface, whereby the lubrication between the cylinder surface and piston ring is improved, the contact time between the cylinder surface and piston ring are reduced and thereby ultimately the wear is reduced.
  • the contact surface of the piston ring which is in frictional contact with the cylinder surface, for example, suitably structured or textured, for example by machining with a laser or other suitable methods known per se, which with a suitable choice of structuring the interaction of Kolbering and cylinder surface additionally positively influence and accelerate the formation of a hydrodynamic lubricating oil film.
  • the partial ring package in particular the top ring, which is arranged closest to the combustion chamber, is configured in such a way that a first partial pressure of the combustion chamber pressure can be formed in a region on an upper side of the first piston ring facing the combustion chamber in the operating state and in one region a second partial pressure of the combustion chamber pressure can be formed at an upper side of the second piston ring facing the combustion chamber in the operating state.
  • the first partial pressure is particularly preferably greater than the second partial pressure and in particular, the combustion chamber pressure may be substantially the sum of a voltage applied across the oil collecting ring pressure drop and the first partial pressure and the second partial pressure, wherein in one of the Practice particularly important embodiment of the first partial pressure preferably between 55% and 95%, in particular about 65% of the combustion chamber pressure is.
  • the pressure relief means is particularly preferably a Druckentlastungsnute and extends the Druckentlastungsnute advantageous in a direction deviating from a radial direction at the bottom of the first piston ring, preferably perpendicular to the piston axis.
  • the pressure relief groove may extend over an entire width of the piston ring.
  • the pressure relief means may also be provided, for example in the form of a pressure relief joint on the first Kolbenringnute.
  • the pressure relief means may also be provided in the form of a pressure relief hole in the first piston ring or in the form of a pressure relief channel to the first Kolbenringnute.
  • the pressure relief holes in the first piston ring or the pressure relief channel on the first Kolbenringnute or even the pressure relief gap extend particularly advantageous in the direction deviating from the radial direction, preferably perpendicular, i. little or little inclined with respect to the piston axis.
  • a piston according to the invention may comprise more than just two piston rings, as will become clear below, in particular.
  • a piston of the present invention comprises only two piston rings, namely the first piston ring and the underlying oil distribution ring, which will be discussed in more detail below.
  • the first piston ring or other present in the piston ring package piston rings with respect to the piston axis cooperating with the cylinder wall asymmetric outer contour, wherein the width of the first piston ring in the direction of the recess preferably increasing gets bigger.
  • the second piston ring is advantageously configured in such a way that it interacts largely pressure-tight with the cylinder wall of the cylinder in the installed and operating state, so that the piston ring package better seals the combustion chamber better against the underside of the piston than the one in the state the art known piston is the case.
  • the recess in the lateral surface of the piston is a special embodiment, an extending between the first piston ring and the second piston ring in a circumferential direction of the piston annular space, in particular a ring groove, in particular extending around the piston axis helical groove.
  • the recess may be formed in particular between the first piston ring and the ⁇ lverteilring and / or between the ⁇ lverteilring and the second piston ring.
  • the recess may also be formed, for example, as a planar recess in the lateral surface of the piston, wherein preferably a plurality of separate planar depressions are present. It is understood that the recess of the invention can also be configured in any other suitable form and arranged between the first and the second Kolbering.
  • the second piston ring may also be absent in a piston according to the invention.
  • a connecting channel possibly provided with a supply reservoir for lubricating oil, which acts on a combustion chamber facing the upper side acted upon by a predetermined portion of the combustion chamber pressure inlet port and an outer peripheral surface in the operating state with the cylinder wall in rubbing Contact stands, intended outlet opening connects.
  • the second piston ring itself is formed as ⁇ lverteilring.
  • the optimized oil distribution ring of the present invention, or the inlet opening of the oil distribution ring is controlled by the controlled blowby, which is generated according to the invention by the first piston ring, controlled with a predeterminable gas pressure.
  • the lubricating oil collected in the connecting channel or in the supply reservoir of the connecting channel is thereby returned to the outside, preferably radially outward, from the oil distributing ring to the cylinder running surface through the outlet opening, which is preferably designed like a nozzle. If the oil distribution ring exceeds the scavenging slots, the connecting channel or reservoir is blown out freely through the scavenging slots, which prevents accumulation of harmful residues.
  • the invention further relates to a piston ring for a piston of a reciprocating internal combustion engine for use in a piston according to the invention, as described in detail in this application.
  • the piston ring according to the invention can be arranged to form a piston ring packing on a piston of the invention, wherein a Druckentlastungsnute is provided on a remote in the installed state a combustion chamber underside of the piston ring, which extends over a predetermined range on the underside of the piston ring.
  • the invention also relates to an oil distribution ring for a piston according to the invention of a reciprocating internal combustion engine, wherein the oil distribution a connecting channel, preferably comprising a supply reservoir for lubricating oil, is provided, which at an in the installed state a combustion chamber upper side acted upon by a predetermined portion of a combustion chamber pressure inlet port and a on an outer peripheral surface, which is in the installation and operating condition with a cylinder wall in frictional contact, provided outlet opening connects.
  • a connecting channel preferably comprising a supply reservoir for lubricating oil
  • Fig. 1 is a first embodiment of a piston according to the invention, which is hereinafter referred to collectively with the reference numeral 1, shown schematically in a sectional drawing in cooperation with the cylinder surface 31 of the cylinder 3.
  • the inventive piston according to Fig. 1 is a piston for a two-stroke large diesel engine 2, which usually has a plurality of cylinders 3, in which cylinder 3, the piston 1 in the installed state according to Fig. 1 a combustion chamber VB limited and arranged along a piston axis A of the piston 1 in the cylinder 3 between a top dead center and a bottom dead center in the axial direction back and forth.
  • a piston ring packing 4 rubbing against a cylinder wall 31 of the cylinder 3 is formed in a manner known per se Fig.
  • first piston ring 41 in a first piston ring groove 411, the first piston ring 41 being provided between the piston crown 101 and a second piston ring 42 arranged in a second piston ring groove 421.
  • an oil distribution ring 43 is provided in an oil ring groove 4301.
  • Bottom 4110 of the first piston ring 41 may be provided a Druckentlastungsnute 4111, which extends over a predetermined range over the entire width b of the piston ring 41 on the underside 4110 of the first piston ring 41.
  • the first piston ring 41 is designed in such a way that in a region on an upper side of the first piston ring facing the combustion chamber VB a first partial pressure P1 of the combustion chamber pressure P can be formed and in a region on an upper side of the second piston ring 42 facing the combustion chamber VB Operating state, a second partial pressure P2 of the combustion chamber pressure P can be formed.
  • the combustion chamber pressure P is the sum of a pressure drop across the ⁇ lverteilring 43 and the first partial pressure P1 and the second partial pressure P2, wherein the first partial pressure P1 is about 65% of the combustion chamber pressure P.
  • the second piston ring 42 is designed such that it interacts largely pressure-tight with the cylinder wall 31 of the cylinder 3.
  • This form clearly favors the controllably adjustable blowby, ie the controlled gas flow past the first piston ring 41.
  • the second piston ring 42 may also be missing or additional piston rings may be provided.
  • Fig. 2a to Fig. 2c show by way of example to illustrate three embodiments of pressure relief grooves 4111 of according to the invention first piston rings 41, wherein the reference numeral F denotes a gas flow through the pressure relief groove 4111.
  • the Druckentlastungsnute 4111 each extends over an entire width b of the inventive piston ring 41, while the pressure relief groove 4111 in the example of Fig. 2c is not formed over the entire width b of the piston ring 41.
  • the pressure relief groove 4111 of the inventive piston ring 41 of Fig. 2b in this case still has a curved course directed in the circumferential direction of the piston ring 41, so that the Druckentlastungsnute 4111 almost tangential, ie almost perpendicular to the radial direction R in the space between the cylinder surface 31 and piston ring 41 opens, creating an even better distribution or turbulence of the gas flow F is reached.
  • Fig. 2d to Fig. 2f show further variants of pressure relief means 4000, 4112, 4113, 4114, which may also be provided either alternatively to Druckentlastungsnute 4111 or in any combination with each other and / or with the Druckentlastungsnute 4111 on a piston according to the invention, which also illustrated recess 5 is of course only optional for the present invention.
  • Fig. 2d shows an example of a first Kolbering 41 of alternatively or additionally to the pressure relief grooves 4111 pressure relief holes 4112 which are also aligned in the tangential direction, ie away from the radial direction.
  • the pressure relief holes 4112 are thereby inclined against the piston axis A in the direction of the second piston ring 42, not shown, whereby the pressurization of the oil distribution ring 43, not shown, of the second piston ring 42 can be further optimized.
  • FIG. 2e a further embodiment of a piston 1 according to the invention is shown, in which at the first Kolberingnute 411 pressure relief joints 4113 are provided, and based on the Fig. 2f Finally, another embodiment with pressure relief channels 4114 is shown schematically, for reasons of clarity on the representation of the oil distribution ring or the first piston ring 41 was omitted in each case.
  • the operation of the pressure relief joints 4113 and the pressure relief passages 4114 is comparable to the operation of the pressure relief joints 4111 and / or the pressure relief wells 4112.
  • Fig. 3a to 3c show various embodiments of recesses 5, 51, 52, 53, which according to the invention are provided somewhere between the first piston ring 41 and the second piston ring 42, wherein the representation of the ⁇ lverteilrings 43, below the first piston ring 41 and / or above the second piston ring 42 is provided, was omitted for reasons of clarity.
  • Fig. 3a a second embodiment of a piston 1 according to the invention shown schematically, in which recess 5, 51 designed in the form of a circumferential around the circumference of the piston 1 annular groove 51. It is understood that in another embodiment. Fig. 3a Also several circumferential annular grooves can be provided in parallel or not parallel advantageous.
  • an inventive piston 1 in the third embodiment of an inventive piston 1 according to Fig. 3b is recess in the form of a circumferential, in relation to the piston axis A helically configured groove 5, 52 realized.
  • the admission of the second piston ring 42 with the second partial pressure P2 can be additionally tuned and adjusted.
  • the recesses 5, 53 are formed in the form of separate area-like depressions 53.
  • Such embodiments can be used advantageously in special cases, possibly also in combination with one of the embodiments.
  • Fig. 3a or Fig. 3b
  • Fig. 4 shows finally in detail a preferred embodiment of a ⁇ lverteilrings 43 of the present invention.
  • connection channel 431 is provided on the oil distribution ring 43, which on an upper side facing the combustion chamber VB can be acted upon by a predeterminable proportion PA of the combustion chamber pressure P inlet opening 4311 and an outer peripheral surface which in the operating state with the in Fig. 4 for reasons of clarity not shown cylinder wall 31 is in frictional contact, provided outlet opening 4312 connects.
  • the oil distribution ring 43 is provided in addition to the first piston ring 41 and the second piston ring 42 in the piston ring package 4.
  • the second piston ring 42 is formed as ⁇ lverteilring 43. It goes without saying that more than one ⁇ lverteilring can be provided in one and the same piston ring package 4.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
EP11175158A 2011-07-25 2011-07-25 Piston et segment répartiteur d'huile pour moteur à combustion interne à piston élévateur Withdrawn EP2551504A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11175158A EP2551504A1 (fr) 2011-07-25 2011-07-25 Piston et segment répartiteur d'huile pour moteur à combustion interne à piston élévateur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11175158A EP2551504A1 (fr) 2011-07-25 2011-07-25 Piston et segment répartiteur d'huile pour moteur à combustion interne à piston élévateur

Publications (1)

Publication Number Publication Date
EP2551504A1 true EP2551504A1 (fr) 2013-01-30

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EP11175158A Withdrawn EP2551504A1 (fr) 2011-07-25 2011-07-25 Piston et segment répartiteur d'huile pour moteur à combustion interne à piston élévateur

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EP (1) EP2551504A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103410626A (zh) * 2013-06-10 2013-11-27 吉林大学 一种带有表面织构形态的内燃机活塞
WO2015113839A1 (fr) * 2014-02-03 2015-08-06 Federal-Mogul Nürnberg GmbH Piston pour moteur à combustion interne
CN109253252A (zh) * 2018-09-07 2019-01-22 浙江安康汽车零部件有限公司 带刮油、回油功能的活塞气环及活塞组件
WO2019034293A1 (fr) * 2017-08-17 2019-02-21 Federal-Mogul Burscheid Gmbh Ensemble segment de piston, piston et moteur à combustion interne
CN113775736A (zh) * 2021-09-06 2021-12-10 上海涟屹轴承科技有限公司 配油环及其齿轮箱配油系统

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB427780A (en) * 1933-10-31 1935-04-30 William Gerhard Godert Godron Improvements in pistons or the like
JPS58172039U (ja) * 1982-05-12 1983-11-17 株式会社リケン ピストンリング
WO1997011295A1 (fr) * 1995-09-22 1997-03-27 Man B & W Diesel A/S Segment de piston pour piston de moteur a combustion interne
US5655433A (en) * 1995-10-10 1997-08-12 Briggs & Stratton Corporation Piston-piston ring assembly and method for reducing engine exhaust emissions
US5996545A (en) * 1997-03-05 1999-12-07 Ing. H.C.F. Porsche Ag Internal combustion engine with a horizontal cylinder
WO2004090389A1 (fr) * 2003-04-10 2004-10-21 Man B & W Diesel A/S Segment de piston pour moteur a combustion interne

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB427780A (en) * 1933-10-31 1935-04-30 William Gerhard Godert Godron Improvements in pistons or the like
JPS58172039U (ja) * 1982-05-12 1983-11-17 株式会社リケン ピストンリング
WO1997011295A1 (fr) * 1995-09-22 1997-03-27 Man B & W Diesel A/S Segment de piston pour piston de moteur a combustion interne
US5655433A (en) * 1995-10-10 1997-08-12 Briggs & Stratton Corporation Piston-piston ring assembly and method for reducing engine exhaust emissions
US5996545A (en) * 1997-03-05 1999-12-07 Ing. H.C.F. Porsche Ag Internal combustion engine with a horizontal cylinder
WO2004090389A1 (fr) * 2003-04-10 2004-10-21 Man B & W Diesel A/S Segment de piston pour moteur a combustion interne

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103410626A (zh) * 2013-06-10 2013-11-27 吉林大学 一种带有表面织构形态的内燃机活塞
CN103410626B (zh) * 2013-06-10 2015-04-22 吉林大学 一种带有表面织构形态的内燃机活塞
WO2015113839A1 (fr) * 2014-02-03 2015-08-06 Federal-Mogul Nürnberg GmbH Piston pour moteur à combustion interne
WO2019034293A1 (fr) * 2017-08-17 2019-02-21 Federal-Mogul Burscheid Gmbh Ensemble segment de piston, piston et moteur à combustion interne
CN109253252A (zh) * 2018-09-07 2019-01-22 浙江安康汽车零部件有限公司 带刮油、回油功能的活塞气环及活塞组件
CN113775736A (zh) * 2021-09-06 2021-12-10 上海涟屹轴承科技有限公司 配油环及其齿轮箱配油系统
CN113775736B (zh) * 2021-09-06 2024-02-09 上海涟屹轴承科技有限公司 配油环及其齿轮箱配油系统

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